Pumps



Bed, 1957 A. SENKOWSKI ETAL PUMPS 3 Sheets-Sheet 1 Filed May 14, 1953INVENTORS. V ALEXANDER SENKOWSK 8i FREDERICK D. COOPER by 642...,

Dec. 17, 1957 A. SENKOWSKI ETAL PUMPS Filed May 14, 1953 3 Sheets-Sheet3' INVENTO ALEXANDER SENKOW a BY FREDERICK D. COOPER ATTOR/VEKS.

PUMPS Alexander Senkowski, Earlsdon, Coventry, and Frederick D. Cooper,Stoke, Coventry, England, assignors to Massey-Harris-Ferguson (Sales)Limited, a British comn y Application May 14, 1953, Serial No. 354,905

Claims priority, application Great Britain May 16, 1952 9 Claims. (Cl.103-169) The invention relates to improvements in pumps and moreparticularly to piston-type pumps foruse in tractor power lift systemsoperating in accordance with the principles taught in the FergusonPatent No. 2,118,180 issued May 24, 1938.

One object of the invention is to provide in a pump of the above generalcharacter improved mechanism for imparting reciprocatory mot-ion to thepump piston or pistons from a rotary driving shaft.

A more specific object is to provide improved mechanism forreciprocating a pump piston through the medium of a crosshead fixed onthe piston and having a connection with a follower rotatably mounted on.an eccentric on a rotatable shaft whereby positive movements areimparted to the piston in both directions while lateral stresses on theparts are reduced to a minimum Another object is to provide a pumpvconstruction in which the pump cylinders and driving shaft areinterrelated so as to reduce the bending moment on the mechanismsconnecting the pistons with the: shaft in the stroke range in which suchbending moments are ordinarily at their maximum.

Still another object is to provide a pump wherein the components arearranged and. interrelated so that the cylinder bores and connectingpassages can. all be formed in the pump body by simple drillingoperations with a resultant simplification of manufacture andsubstantial reduction in cost.

A further object is to provide improved means for efficiently andpositively lubricating the moving parts of the pump.

It is also an object of the invention to provide a pump which is simplein construction and extremely rugged and dependable, which has amplecapacity to meet the requirements of a tractor hydraulic lift system andwhich is sufficiently compact and appropriately shaped to find readyaccommodation within the tractor body.

Other objects and advantages of the invention will become apparent fromthe following detailed description of the preferred embodimentillustrated in the accompanying drawings in which:

Figure 1 is a side elevational view ofa pump and control valve assemblyembodying the features of the inven tion with parts broken away to showdetails of construction.

Fig. 2 is a transverse sectional view through the pump taken in avertical plane substantially on the line 2-2 of Fig. l.

Fig. 3 is a sectional view taken in a plane substantially on the line3-3 of Fig. 2..

Fig. 4 is a sectional view through the control valve mechanism taken ina vertical plane-substantially on the line 4-4 of Fig. 1.

Fig. 5 is a fragmentary sectional view taken through the valve mechanismand pump body substantially on the line 5-5 of Fig. 1.

Fig. 6 is a sectional view through the pump body taken in a verticalplane substantially on the line 6-6 of Fig. 1.

nited States Patent 0 Fig. 7 is a fragmentary sectional view taken in avertical plane substantially on the line 77 of Fig. 1.

Fig. 8 is a fragmentary sectional view taken in a horizontal planesubstantially on the line 8-8 of Fig. 1.

Fig. 9 is a fragmentary sectional viewtaken in a horizontal planesubstantially on the line 9-9 of Fig. 1-.

While we have shown and will herein describe the invention as embodiedin a particular form of pump, it is to be understood that this detaileddisclosure isnot in-' tended to limit the invention but merely toillustrate what is now believed to be its preferred form and that it isour intention to cover all modifications and alternative constructionsfalling withinthe spirit and scope of the invention as expressed in theappended claims;

For purposes of illustration, the invention has been shown as embodiedin a pump particularly suitable for use in a tractor hydraulic liftsystem of the same general type as that employed in the Fergusontractor. The exemplary pump, by reason of its size, shape and capacity,is especially well suited for use in the tractor disclosed in theco-pending application of Alexander Senkowski and Arthur E. Lynes,Serial No. 354,904, filed May 14, 1953-, and finds ready accommodationwithin the body of such tractor.

In general, the exemplary pump has a body 10 formed with a plurality ofmain cylinder bores 11 each having a piston 12 reciprocable therein.Reciprocation of the pistons in the cylinders is efiected through themedium of a shaft 13 extending across the upper ends of the cylindersand rotatably supported at opposite ends by bearings carried on theupper end of the pump body. Driving mechanisms 15 of novel andadvantageous construction, described in detail hereinafter, operativelyconnect the shaft 13 with the respective pistons 12. The pump body 10 isformed with suitable passages and valves accommodating fluid flow to andfrom the cylinders 11 in the operation of the pump.

A housing 16 attached to one end of the pump body and forming therewitha unitary structure, encloses control valve mechanism for controllingthe operation of the pump. More particularly, the control valvemechanism is associated with the pump intake and pump operation isstarted or stopped by opening or closing the intake, as taught in theFerguson patent above referred to.

An auxiliary pumping device 17 provided in the pump body acts to supplyoil under pressure to certain moving parts of the pump for lubricationso that the pump may be operated dry, that is, without being submergedin a body of oil.

In accordance with the invention, the pump body 10 and other componentsof the pump are constructed and arranged to afford compactness andto-simplify manufacture and assembly. As shown in Figs. 1, 2 and 5 ofthe drawings, the pump body comprises an elongated flat and relativelynarrow intermediate section 20 disposed generally vertically and havinga generally horizontal section 21 extending rearwardly therefromsomewhat above its lower end. An integral depending flange or skirt 22supports and reinforces the outer end of the section 21. Theintermediate and horizontal sections 20 and 21 are preferably formed asintegral parts of a unitary casting and have formed integrally therewithupright end sections 25 and 26 of somewhat greater width and extendingabove the intermediate section.

The end sections 25 and 26' of thepump body cooperate with bearingblocks 27 to rotatably support the shaft 13. As shown in Fig. 6, theblocks 27 are removably secured to the upper ends of the end sections byscrews 28 and the blocks and adjacent portions of such end sections areformed to provide recesses for bearings 29 journaling the shaft 13 atopposite ends. One of the end sections, in this instance, the section26, has a fiat pad 30 machined on its outer face for the mounting of thevalve housing 16 which may be secured thereto as by machine screws 31.

End section 25 of the pump body and valve housing 16 preferablyterminate at their lower ends in outturned flanges 32 (Fig. 6) forsupporting the pump and valve assembly. The exemplary pump is designedto be supported within the body of a tractor as by bosses 33 extendingupwardly from the bottom 34 of the tractor crank case. Machine screws 35inserted through holes in the bosses and threaded into tapped holes inthe flanges 32 securely anchor the pump and valve assembly in place inthe tractor.

The intermediate section of the pump body is formed with one or more ofthe cylinder bores 11, there being three such bores in the exemplarypump although it will be appreciated that the number of cylinders to beprovided is a matter of choice. The bores 11 extend entirely through theintermediate section 20 opening in its narrower upper and lower faces asshown in Fig. 2. Each bore is stepped adjacent its lower end so as topresent axially spaced downwardly facing shoulders 40 and 41, thepurpose of which will become apparent as the description proceeds.

Extending longitudinally of the body section 21 are two passages 42 and43 opening in the pad 30 for communication with passages in the valvehousing 16 and respectively forming inlet and outlet passages for thepump cylinders 11. As shown in Fig. 2, the inlet passage 42 is locatedso as to intersect the cylinder bores 11 below the shoulders 40. Theoutlet passage 43 is located above the inlet passage and at one side ofthe cylinders 11. Communication with the cylinders is by way of crosspassages 44 drilled from the rear face of the body section 21 tointersect the passage 43 and open into the cylinder bores.

Communication between the inlet passage 42 and the cylinders 11 iscontrolled by inlet valve assemblies 45, one of which is fitted into thelower end of each cylinder bore. As shown in Fig. 2, the valve assembly45 comprises a guide member 46 adapted to abut against the shoulder 40in the cylinder bore and having drilled passages 47 establishingcommunication between the inlet passage 42 and a chamber 48 in the upperend of the guide member. Communication between the chamber 48 and thecylinder is controlled by a movable valve member having a head 49coacting with a valve seat encircling the chamber. The valve member isguided between open and closed positions by a stem 50 extendingdownwardly from the head 49 and slidable in a central bore in the guidemember 46. A compression spring 51 interposed between the lower end ofthe guide member and an abutment such as a collar 52 fixed on the end ofthe valve stem urges the valve to closed position but permits it to openwhen necessary to admit fluid to the cylinder with which it isassociated.

A plug 53, recessed for the accommodation of the valve stem and itsspring and threaded into the lower end of the cylinder bore 11, abutsthe guide member 46 and wedges it into sealing engagement with theshoulder 40. The shoulder 41 in this instance defines the limit positionof the plug. As shown, the plug is formed with a slot 54 or othersuitably shaped recess for engagement with a tool, such as a screwdriver, by which the valve assembly may be removed for inspection,cleaning or repair.

Communication between the outlet passage 43 and the cylinder bores 11 iscontrolled by outlet valve assemblies 55, one of which is fitted intoeach of the cross passages 44. The valve assembly in its preferred formcomprises a movable valve member having a head 56 adapted to engage aseat formed by a rearwardly facing shoulder 57 in the bore 44. A stem 58extends rearwardly from the valve head and is guided in a flanged guidemember 59 held against the shoulder 60 in the bore 44 by a plug 61threaded into the bore. A compression spring 62 interposed between thevalve head 56 and the flange on the guide member urges the valve toclosed position. The plug 61 like the plug 54 has its outer end formedfor convenient engagement with a tool such as a screw driver by whichthe valve assembly may be removed for cleaning or servicing.

Each of the plungers 12 is dimensioned for a working fit in its cylinder11 so that as it is moved upwardly in the cylinder, fluid will be drawnfrom the passage 42 through valve 45 into the cylinder. In the downwardmovement of the plunger, the fluid is trapped by closure of the valveand is forced out of the cylinder through the valve 55 and outletpassage 43. As shown in Fig. 2, the piston 12 may be formed with aseries of circumferential grooves 63 operative to trap a quantity of oiland insure adequate lubrication of the cylinder wall when the pumpingaction is stopped, that is, when the inlet passage 42 is closed to shutoff the supply of fluid.

Reciprocation of the valve plungers 12 is eflected by the shaft 13acting through the drive mechanisms 15, as mentioned heretofore. Forthis purpose, each of the pistons 12 is provided at its upper end with atransverse member or crosshead 65 fixed to the piston intermediate itsends as by a pin 66. The drive shaft 13 is formed with a plurality ofeccentrics 67, one for each cylinder, and these eccentrics are locatedin alinement with the respective cylinders. Rotatably mounted on eacheccentric is a follower member or slipper 70 having a pair of laterallyspaced guide elements 71 depending from its lower end and dimensioned toslidably receive the crosshead 65 and to confine its movements relativeto the slipper in a direction normal to the axis of the piston. In otherwords, the guides and crosshead operatively connect the slipper with thepiston in a manner such that positive movements are imparted to thepiston in both directions, that is, into and out of the cylinder as theslipper is traversed around a circular orbit in the rotation of theeccentric upon which it is mounted. The crosshead, of course, slidesback and forth in the guides as the slipper follows its orbital path.

The crosshead 65 is preferably rectangular in cross section anddimensioned to present a bearing surface of relatively large area on itsupper face for receiving the thrust of the slipper 70. In the particularembodiment illustrated, a bearing plate 72 of bronze or other suitablebearing material is interposed between the bearing surfaces on thecrosshead and the slipper to reduce friction. However, if it is desiredto further simplify the pump construction, the bearing plate may beomitted in which case the crosshead is desirably made of chilled castiron and the slipper of bronze with lead flashed on the coacting bearingsurfaces. When the bearing plate is used, it is held in place by a dowelpin 73 fitted into the slipper.

For convenience of manufacture and assembly, the follower or slipper 70is constructed in two sections adapted to meet in a substantiallyvertical plane through the axis of the eccentric 67. The two sectionsare secured together in any suitable manner as by machine screws 75.Preferably, a bearing ring 76 is interposed between the eccentric andthe slipper, the ring being split along a line at right angles to thecylinder axis and installed with the split displaced approximatelydegrees from the junction between the two parts of the slipper torelieve the latter of a portion of the stresses developed by the thruston the piston. Means such as a dowel pin 77 may be provided forretaining the hearing ring in place.

In accordance with another aspect of the invention, the bending momentimposed on the crosshead 65 at the point of maximum thrust from theslipper 70 is substantially reduced by locating the drive shaft 13 withits axis offset toone side of the axes of the cylinders 11. As shown inFig. 2, the offset is such that the cylinder axis when extended passesapproximately midway between the axis of the shaft and the center of theeccentric 67. As maximum thrust occurs when the piston 12 issubstantially at its midstroke, as shown in Fig. 2, it will be evidentthat the bending effect on the crosshead at this point will bematerially reduced.

The invention also contemplates the provision of a novel arrangement forpositively lubricatingthe bearings for the shaft 13 and other movingparts at the upper end of the pump structure so that the pump may beoperated dry, that is, with the upper portion above the level of the oilin the sump or compartment of the tractor body in which it is installed.As indicated heretofore, a supply of lubricating oil under pressure isfurnished by the auxiliary pumping device 17 which may comprise a smallplunger-type pump adapted to be driven from the pump drive shaft 13.

Referring to Figs. 6-9 of the drawings, the auxiliary pump 17 comprisesa cylinder formed by a generally upright hole 81 drilled in theintermediate body section 20 closely adjacent the end section 25. Aplunger 82 having a working fit in the cylinder 81 is operativelyconnected by a pin 83 with the crosshead 65 of the adjacent pump piston.The plunger 82 therefore reciprocates in its cylinder 81 in synchronismwith the reciprocation of the adjacent pump piston.

An inlet for the cylinder 81 is formed by a vertical passage 84 drilledin the body section 25 and opening at the bottom thereof to receive oilfrom the compartment in which the pump is mounted. Adjacent its upperend the passage 84 is connected by a drilled transverse passage 85 withthe cylinder 81 preferably at a point slightly above the midstroke ofthe plunger 82. This allows the plunger to trap oil in the bottom of thecylinder in its downward stroke and eliminates the need for an intakevalve. A threaded plug 86 closes the outer end of the cross passage, asshown in Fig. 8.

Fluid under pressure is discharged from the cylinder 81 through adrilled passage 87 in the pump body section 25 which passagecommunicates with the cylinder through a drilled cross passage 88 (Fig.9) having its outer end closed by a threaded plug 89. The cross passage88 is formed with a shoulder defining a seat for a ball check valve 90adapted to restrict oil flow through the passages to one direction, thatis, outwardly from the cylinder 81. A spring 91 interposed between theend of the plug 89 and the ball 90 urgesthe latter to closed position.

At its upper end, the passage 87 opens into an annular channel 92(Fig. 1) formed in the body section 25 and bearing block 27 so as toencircle the shaft 13. It will be observed that the bearing 29 for theshaft is in the form of two rings located on opposite sides of thischannel. The channel communicates through radial holes 93 in the shaftwith a central lubricating passage 94 extending axially through theshaft 13. This passage is preferably drilled from one. end of the shaft(the left end, as viewed in Fig. 1), and the open end of the passage isclosed by a ball-type relief valve 95 urged to closed position by aspring 96.

Radial passages 97 in the shaft 13 lead from the central passage 94 tothe bearing surfaces of the eccentric 67 and also to a space between thebearings '29 at the right end of the shaft. Passages 97' (Fig. 2) ineach slipper 70 conduct oil from the eccentric bearing to the bearingsurfaces of the slipper and the associated crosshead 65. Thus thebearings for the shaft, the hearing surfaces for the eccentric andslippers and the bear ing surfaces for the crossheads are continuouslysupplied with oil under pressure to ensure adequate lubricating wheneverthe pump is operated.

In the exemplary pump the shaft 13 is arranged to be driven through themedium of a gear 98 keyed to the projecting end of the shaft. Thegear islocated closely adjacent the end section 25 and in a position to receiveoil forced through the bearing 29 for the shaft. Such oil is caught in acircumferential groove 99 in the inner face of the gear and thrownoutwardly at relatively high velocity through diagonally disposedpassages 100 in the body of the gear. Adjacent moving parts of thetractor are thus lubricated.

The control valve mechanism enclosed in the housing 16 is particularlydesigned for operation in systems of the type disclosed in the Fergusonpatent previously referred to. Structurally, it is generally similar tothe valve mechanism disclosed in the co-pending application of AlexanderSenkowski and Witold Czarnocki, Serial No. 126,603, filed November 10,1949 now Patent No. 2,763,528, issued March 30, 1954. As shown in Figs.1 and 4, the valve mechanism comprises a movable valve member or plunger101 reciprocable in a liner sleeve 102 fitted into a bore 103 in thehousing 16. The sleeve 102 is in communication at its lower end with afluid inlet passage 104 formed in the lower section of the housing whichpassage is connected by a conduit 105 of relatively large diameter witha sump or reservoir in the tractor body which holds a supply of fluidfor use in the hydraulic system. Ports 106 in the sleeve open into anannular chamber 107 in the valve housing which is in communication withthe pump inlet passage 42. Plunger 101, by opening or closing the ports106, admits fluid to the pump or shuts off the fluid supply when thepumping operation is to be stopped.

The valve housing 16 is also formed with a horizontal passage 110 (Figs.4 and 5) communicating through a branch passage 111 with the outletpassage 43 in the pump body as shown in Fig. 5. A check valve 112 guidedin a sleeve 113 and urged to closed position by a s ring 114 preventsfluid flow from the valve to the cylinders while permitting flow in theopposite direction. The passage 110 opens to an annular chamber 115encircling the sleeve 102 and also to a vertical passage 116 which turnsforwardly at its lower end and is connected by a conduit 117 (Fig. 1)with the actuator of the tractor power unit. Pressure fluid from thepump is thus delivered to the actuator by way of the passages abovementioned, and the conduit 117.

To provide for exhaust of fluid from the actuator, the sleeve 102 isformed with radial ports 118 communicating with the ch mber 115. Whenthe plunger 101 is shifted downwardly from the position in which it isshown in the drawings, the ports 118 are uncovered to permit flow offluid into a chamber 119 in the upper part of the valve housingconnected by a passage 120 (Figs. 4 and 5) with the passage 104 which,as before explained, is connected to the sump. The chamber 119 is closedat its upper end by a suitable sealing member 121 fitted into the upperend of the valve member and apertured to slidably receive an extensionsleeve 122 fixed to the upper end of the valve plunger.

As will be seen by reference to Figs. land 4, the ports 106 and 118 arespaced apart so that the plunger 101 closes both sets of ports when inthe neutral position in which it is shown in the drawings. The pumptherefore operates idly, that is, it delivers no fluid, and exhaust offluid is blocked by the closed ports 118. As the plunger is movedupwardly, ports 118 remain closed and the ports 106 are openedprogressively to admit fluid to the suction side of the pump. The pumpaccordingly delivers fluid under pressure through the passages 43, 110,116 and conduit 117 to the actuator.

Movement of the valve plunger 101 in the opposite direction, that is,downwardly from the neutral position, opens the ports 118 while keepingthe ports 106 closed. The pump is therefore idle and fluid is exhaustedfrom the actuator and returned to the sump by way of the conduit 117,passages 116 and 110, chamber 115, ports 118, chamber 119, passages 120and 104 and conduit 105. Ports 118, which are preferably of relativelysmall cross sectional area, serve to meter the exhaust from the actuatorand thus determine the maximum rate at which fluid is permitted toexhaust from the actuator under the gravity load imposed on it by theimplement attached to the tractor hitch linkage. Precise regulation ofthe discharge rate is facilitated by tapering the upper end of the valveplunger, as indicated at 123.

The plunger 101 is shifted between its various positions by controlmechanism on the tractor which includes a lever (not shown) having oneend confined between spaced fianges 124 on the extension sleeve 122. Toprevent the valve plunger from sticking, provision is made forcontinuously oscillating it about its longitudinal axis. In theexemplary embodiment, oscill tion is effected through the medium of atorsionally flexible rod 125 secured at its lower end to the plunger 101as by a pin 126 adjacent its junction with the extension sleeve. Theupper end of the rod is formed with radially projecting arms 127engageable in longitudinal grooves in the inner wall of a sleeve member128 journaled in a bracket 129 bolted or otherwise rigidly secured tothe end of the pump body. The sleeve 128 has a fork 130 at its upper endembracing the pump drive shaft 13 and carrying follower rolls 131engaging in a cam groove 132 in the enlarged end portion of the shaft.This groove is disposed in a plane oblique to the axis of the shaft andconsequently rotation of the shaft is effective to oscillate the sleeve128 about its axis and oscillating movements are transmitted to thevalve plunger 101 through the torsion rod 125.

Provision is made for lubricating the cam groove and follower 131 fromthe pressure feed system of the pump described heretofore. To this end,the drive shaft 13 is formed with an inclined passage 133 (Fig. 1)communicating with the oil space between the bearing rings 29 for theright end of the shaft. The passage 133 extends to an axial passage 134in the shaft which has radial branches 135 (Fig. 4) opening at thebottom of the cam groove.

It will be apparent from the foregoing that the invention provides apump of novel and advantageous construction particularly well adaptedfor use in tractor hydraulic systems. By reason of its simpleconstruction and the novel relationship of its components, the pump maybe manufactured at low cost. It is rugged and dependable and capable offunctioning with a minimum of attention under the severe operatingconditions encountered in a tractor environment.

The novel drive mechanism provided for driving the pump plungers fromthe rotary drive shaft is advantageous in minimizing strains on theparts with the consequent reduction in wear and material lengthening oftheir useful life. Furthermore, the novel arrangement provided forforced lubrication permits the pump to be installed with the majorportion of its moving parts located above the oil level in the tractorbody.

We claim as our invention:

1. A pump comprising, in combination, an elongated generally fiatcasting having a series of main cylinder bores disposed in parallelrelation in a straight line, a drive shaft extending across the ends ofsaid cylinders and rotatably supported at opposite ends in bearingscarried on said casting, eccentrics on said shaft positioned adjacentthe respective cylinders, a slipper rotatably mounted on eacheccentricand having means defining a guideway disposed transversely ofthe axis of the adjacent cylinder, a piston rcciprocable in eachcylinder, a crosshead operatively associated with each piston andengaging in the guideway of the adjacent slipper for transmittingreciprocatory movement to the piston, an auxiliary cylinder bore formedin said casting at one end of the line of main cylinder bores, saidauxiliary cylinder bore having an inlet communicating with a source oflubricating oil and a branched outlet extending to the bearings for saidshaft, said slippers and to said guideways, a plunger reciprocable insaid auxiliary cylinder bore, and means operatively connecting saidplunger with the crosshead of the piston in the adjacent main cylinderbore for reciprocation thereby.

2. A pump comprising, in combination, an elongated generally fiatcasting having a series of generally vertical cylinder bores arranged ina line and opening at opposite ends in the narrow ends of the casting, apiston reciprocable in each cylinder bore, a shaft extending across saidcylinder bores and rotatably supported at opposite ends, a series ofeccentrics on said shaft alined with the respective cylinder bores,means connecting said eccentrics to said pistons for reciprocating thelatter in response to the rotation of said shaft, said casting having afirst horizontal bore intersecting said cylinder bores at their lowerends and defining an inlet passage for the cylinder bores, valvemechanism removably mounted in the lower end of each cylinder borecontrolling communication between said inlet passage and the cylinderbore, said casting having a second horizontal bore disposed along oneside of the cylinder bores and connected with the latter by transversepassages, said second bore defining an outlet passage for the cylinderbores, valve mechanism in each transverse passage controllingcommunication between the cylinder bores and said outlet passage,control valve mechanism including a housing secured at one end of saidcasting, said housing defining a valve chamber and having drilledpassages connecting said inlet and said outlet passages respectivelywith said valve chamber.

3. A pump comprising, in combination, a body adapted to be mounted in anoil sump with its upper end above the oil level in the sump, said bodyhaving an upright main cylinder bore, a piston reciprocable in saidcylinder, a shaft extending transversely across the upper end of saidcylinder, bearings on said body rotatably supporting said shaft atopposite ends, an eccentric on said shaft, a follower member rotatablymounted on said eccentric, said shaft having a passage for conveyinglubricant to said bearings and said follower members, a crossheadoperatively connecting said follower member with said piston, said pumpbody having at one end a generally upright auxiliary cylinder bore, aplunger reciprocable in said auxiliary cylinder bore, means operativelyconnecting said plunger with said crosshead for reciprocation with saidpiston, an inlet passage extending from said auxiliary cylinder bore tothe bottom of the pump body for admitting oil to the cylinder bore fromthe sump in which the pump body is mounted, and means defining an outletpassage in said pump body connecting said auxiliary cylinder bore withthe lubricant passage in said shaft, said plunger being operative in itsreciprocation to draw oil through said inlet passage and deliver itunder pressure to said lubricant passage.

4. A pump comprising, in combination, a body adapted to be mounted in anoil sump with its upper end above the oil level in the sump, said bodyhaving an upright main cylinder bore, a piston reciprocable in saidcylinder, a shaft extending transversely across the upper end of saidcylinder, bearings on said body rotatably supporting said shaft atopposite ends, an eccentric on said shaft, a follower member rotatablymounted on said eccentric, said shaft having passages therethrough forconveying lubricant to said bearings and to said follower member, acrosshead operatively connecting said follower member with said piston,said body having at one end a generally upright auxiliary cylinder bore,a plunger reciprocable in said auxiliary cylinder bore, meansoperatively connecting said plunger with said crosshead forreciprocation with said piston, means defining an oil inlet passage forsaid auxiliary cylinder bore having an inlet opening adjacent the lowerend of the pump body and openng into the auxiliary cylinder boreapproximately midway of the stroke of said plunger, and means definingan outlet passage for said auxiliary cylinder bore opening from thebottom of the cylinder bore and extending upwardly to communicate withthe lubricant passages in said shaft.

5. A pump comprising, in combination, an elongated body casting having aseries of cylinder bores opening on its narrow end, a pistonreciprocable in each cylinder, a shaft extending across the cylinderbores, bearings rotatably supporting said shaft at opposite ends on saidcasting, means including eccentrics on s id shaft and members rotatablymounted on said eccentrics for reciprocating said pistons in therotation of said shaft, an auxiliary lubricating pump including acylinder formed in said casting and having a working piston reciprocablewith one of the first mentioned pistons, said auxiliary pump beingoperable to deliver oil under pressure to a channel encircling saidshaft, said shaft having a longitudinal lubricating passage with radialbranches communicating with said channel, said bearings and theeccentrics, and a gear wheel on said shaft for rotating the same, saidgear wheel being located closely adjacent one of said hearings toreceive oil therefrom having radial passages adapted to throw off theoil so received to lubricate adjacent moving parts.

6. A pump as defined in claim 1 including a spool type valve membershiftable axially for controlling operation of the pump, drive mechanismincluding a cam on the drive shaft and a follower cooperating with saidcam to oscillate said valve member about its axis, said drive shafthaving an oil conducting passage extending from the outlet of theauxiliary cylinder to said cam.

7. A pump as defined in claim 4 in which said shaft has a plurality ofradial passages in communication with the lubricant passagetherethrough, and in which communication between the outlet passage forthe auxiliary cylinder bore and the lubricant passages through the pumpshaft is effected through the medium of an annular chamber in one of theshaft bearings connected to the outlet passage for the auxiliarycylinder bore, and to said plurality of radial passages in said shaft.

8. In a pump having a body casting with a series of upright cylinderbores therein, passages in said body defining fluid inlets and outletsfor said cylinder bores, pistons reciprocable in said cylinder bores, ashaft extending across said cylinder bores, bearings mounted on saidbody rotatably supporting said shaft at opposite ends, and meansinterposed between said pistons and said shaft operative in the rotationof said shaft for reciprocating said pistons, said shaft having passagestherethrough for conveying lubricant to said bearings and to saidreciprocating means, the combination of means for lubricating saidbearings and said reciprocating means comprising an auxiliary pumpformed by three generally upright bores drilled in the pump body andconnected by two transverse drilled bores, one of said upright boresdefining an auxiliary purp cylinder, another of said upright boresdefining an inlet passage connecting said one bore with a fluidreservoir, the third one of said upright bores defining an outletpassage for connecting the auxiliary cylinder with the lubricantpassages in said shaft, a check valve in said outlet passage allowingflow only from said auxiliary pump cylinder to said outlet passage, 21plunger reciprocable in said auxiliary pump cylinder, and means forreciprocating said plunger in response to the rotation of said shaft.

9. A pump as defined in claim 4 in which the lubricant passages in theshaft include an axially-extending passage and a series ofradially-extending outlet passages communicating with saidaxially-extending passage, and a relief valve closing one end of saidaxially-extending passage.

References Cited in the file of this patent UNITED STATES PATENTS1,964,245 Benedek June 26, 1934 2,081,224 Coberly May 25, 1937 2,118,180Ferguson May 24, 1938 2,288,963 Von Tavel July 7, 1942 2,324,291 DodgeJuly 13, 1943

